Guideway station for a rotary guideway switch
CROSS REFERENCE TO RELATED APPLICATIONS 
     The following related and concurrently filed and coassigned patent applications are hereby incorporated by reference: 
     U.S. Pat. application No. 07/711,723, filed concurrently, entitled ROTARY GUIDEWAY SWITCH FOR PEOPLE MOVER SYSTEMS and filed by Thomas J. Burg, William K. Cooper, Robert J. Anderson, Ronald H. Ziegler and John W. Kapala. 
     U.S. Pat. application No. 07/213,206, filed concurrently, W.E. 54,453 entitled ELECIRIC COUPLING FOR ROTARY GUIDEWAY SWITCH and filed by Thomas J. Burg. 
     U.S. Pat. application No. 07/211,734, filed concurrently, W.E. 54,454 entitled SAFELY LOCKING STRUCTURE FOR A ROTARY GUIDEWAY SWITCH and filed by Thomas J. Burg, William K. Cooper Robert J. Anderson. 
     U.S. Pat. application No. 07/211,726, filed concurrently, W.E. 54,456 entitled ROTARY GUIDEWAY SWITCH HAVING SINGLE TIRE PATH LOADING and filed by Thomas J. Burg, William K. Cooper, Robert J. Anderson, Ronald H. Ziegler and John W. Kapala. 
     U.S. Pat. application No. 07/211,735, filed concurrently W.E. 54,457 entitled SELF-ALIGNING ROTARY GUIDEWAY SWITCH and filed by Thomas J. Burg. 
     U.S. Pat. application No. 07/211,610, filed concurrently, W.E. 54,458 entitled SINGLE TURNOUT ROTARY GUIDEWAY SWITCH AND A DUAL LANE CROSSOVER STATION EMPLOYING THE SAME and filed by Thomas J. Burg, William K. Cooper, Robert J. Anderson, Ronald H. Ziegler and John W. Kapala. 
     U.S. Pat. application No. 07/211,736, filed concurrently, W.E. 54,459 entitled DOUBLE TURNOUT ROTARY GUIDEWAY SWITCH and filed by Thomas J. Burg, William K. Cooper, Robert J. Anderson, Ronald H. Ziegler and John W. Kapala. 
     U.S. Pat. application No. 7/211,721, filed concurrently, entitled IMPROVED ELECTRIC, GUIDANCE, AND TIRE PATH CONFIGURATION FOR A PEOPLE MOVER GUIDEWAY and filed by William K. Cooper, Thomas J. Burg, and John W. Kapala. 
     U.S. Pat. application No. 07/211,724, filed concurrently, entitled ROTARY GUIDEWAY SWITCH HAVING GUIDEBEAM AND/OR ELECTRIC RAIL STRUCTURE LOCATED ABOVE AND BETWEEN GUIDEWAY TIRE PATHS, filed by Thomas J. Burg, William K. Cooper, Robert J. Anderson, Ronald H. Ziegler and John W. Kapala. 
     BACKGROUND OF THE INVENTION 
     The present invention relates to people mover systems and more particularly to guideway switches for such systems. 
     In cross referenced basic patent application Serial No. 211,723 (WE 53893), a general background description is presented and there is disclosed the structure and operation of a new rotary guideway switch and a new guideway configuration for people mover systems. That disclosure embodies a plurality of basic and improvement inventions and accordingly a family of patent applications, including the present application and those applications listed in the Cross-Reference section, are being filed concurrently in correspondence to the respective inventions. 
     The present patent application is directed to guideway station structure that houses a rotary guideway switch for vehicle switching operation. 
     SUMMARY OF THE INVENTION 
     A switching station for a people mover guideway has a predetermined tire path, guidebeam and electric rail configuration. The switching station routes a transit car from an entry guideway path to either of two exit guideway paths or vice versa. 
     The station includes a guideway section structured at each of its entry and exit points to provide the predetermined guideway configuration including a pair of spaced tire running surface paths for cars operating in the people mover system. The guideway section has an elongated switch pit located within the guideway under a reference plane through the tire running surfaces and extending longitudinally along the tire running surfaces and laterally between the tire running surfaces. 
     An elongated rotary switch frame member is disposed in the switch pit and assembled with the guideway section for alignment with the guideway paths. The frame is provided with guidebeam, electric rail and tire path structure on one side compatibly with the guideway configuration to route a car from the entry path to a first of the two exit paths. The switch frame member further has guidebeam, electric rail and tire path structure on another side compatibly with the guideway configuration to route a car from the entry path to the second of the two exit paths. 
     First and second fixed frames are supported in the pit at opposite ends of the switch frame. Supporting shafts for switch rotation and locking means are supported by the fixed frames. Hydraulic actuator means for the locking and shaft means are also supported by the fixed frames. 
     The switch frame has its one side aligned with the entry and the first exit guideway path in the first frame position with its other side facing downwardly and stored vertically below the reference plane. The switch frame has its other side aligned with the entry and the second exit guideway path in the second frame position with its one side facing downwardly and stored vertically below the reference plane. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     The invention is described below the reference to the accompanying drawings, a brief description of which follows. The Figure numbers of a sectional view are keyed to reference planes denoted by Roman numerals and letters. For example, the sectional view of FIG. 3A is taken through reference plane III A in FIG. 3. 
     FIG. 1 shows a schematic diagram of a guideway layout for a people mover system having rotary guideway switches made and operated in accordance with the principles of the invention; 
     FIG. 1A shows an elevational view of a car of the type employed on the guideway of FIG. 1; 
     FIG. 1B highlights the guideway configuration at a typical cross section of the guideway with a vehicle on it; 
     FIG. 1C shows a cross section of a dual lane portion of the guideway at a switch location thereby highlighting the configuration of the rotary guideway switch and its match with the guideway configuration; 
     FIG. 2A shows a top plan view of a single turnout rotary guideway switch structured in accordance with the invention and positioned in its tangent or main lane position in a lane turnout implementation of the invention; 
     FIG. 2B shows the single turnout switch of FIG. 2A in its turnout position; 
     FIG. 2C is a top plan view showing a more detailed top plan view of a general assembly of the single turnout, rotary guideway switch positioned in its main lane position; 
     FIG. 3 is similar to FIG. 2C but a part of the guideway switch is taken away to show a pit for the movable switch part and other switch equipment: 
     FIGS. 3A through 3ML show respective views that are taken along the indicated reference planes in FIG. 3 and show various structural features of the switch pit; 
     FIG. 3N1 and 3P1 are sectional views along the indicated reference planes in FIG. 3B, and FIGS. 3N2 and 3P2 are side views of FIGS. 3N1 and 3P1, respectively. 
     FIG. 4 shows a top plan view of a single turnout rotary frame assembly that includes a portion of the fixed frame supports and a movable part of the guideway switch; 
     FIGS. 4A and 4B are views taken along the indicated reference planes in FIG. 4 to show the manner in which longitudinal rotary frame expansion is enabled by rolling or floating end beam support provided for the rotary frame by a point end shaft and with vertical support provided at both ends of the frame; 
     FIGS. 4C and 4D respectively are elevation and broken away top plan views of one of the frame end beams which receive lockpin and shaft support for the switch frame; 
     FIG. 4E and 4F show schematic load diagrams illustrating the operation of the load support arrangement for the switch; 
     FIG. 5 is a top plan view of the general assembly of the single turnout rotary guideway switch, i.e. the assembly of the movable switch portion with frog and point end equipment frames; 
     FIGS. 5A through 5D show various enlarged views taken along the indicated reference planes in FIG. 5 to illustrate the rotational support shaft and lockpin operating systems; 
     FIG. 5E is a similar view as 5D showing an inactive switch. 
     FIGS. 6-1F to 6-3F, 6AF-6FF, 6-1P to 6-3P and 6AP-6BP show various views of the frog and point end equipment frames which support the movable switch member and the hydraulic equipment that operates the guideway switch with FIGS. 6AF-6FF and 6AP-6BP being sections through the indicated reference planes in FIGS. 6-1F and 6-1P, respectively; 
     FIG. 7 shows a schematic diagram of an electrohydraulic system employed to operate and control the rotary guideway switch; 
     FIG. 8A shows a top plan view of an additional embodiment of the invention, i.e. a double turnout rotary guideway switch with its right turnout side facing upwardly; 
     FIG. 8B shows a switch pit for the double turnout switch embodiment, i.e. a view similar to FIG. 8A with the movable switch member taken away; 
     FIGS. 8BA through 8BF show various double turnout switch pit views taken along the indicated reference planes in FIG. 8B (some views as indicated by some of the reference planes are identical with those shown in the FIG. 3 series of drawings; 
     FIG. 8C shows a top plan view of the general assembly of the double turnout guideway switch; 
     FIGS. 8CA through 8CG show various equipment views taken along the indicated reference planes in FIG. 8C; 
     FIG. 8D shows the right turnout side of a switch frame assembly for the double turnout guideway switch; 
     FIGS. 8E and 8EA through 8EH respectively show a top plan view of the double turnout switch frame and various views taken along the indicated reference planes in FIG. 8E; 
     FIGS. 8EJ-8EK2 and 8EN and 8EP-8ES show various views highlighting rotation stop structure for the double turnout switch embodiment with FIGS. 8EJ1, 8EJ2, 8EK1, 8EK2, 8EQ and 8ES being sectional views along the indicated reference planes; and 
     FIGS. 9A1 through 9B2 show various views of rotation stop structure for the single turnout switch embodiment with FIGS. 9A2 and 9B2 being sectional views along the indicated reference planes. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     GUIDEWAY SYSTEM 
     More particularly, there is shown in FIG. 1 a people mover system 10 in which the present guideway switch invention is embodied. The system 10 is a schematic representation of Phase 1 of a people mover system being commercially supplied by the assignee of the present invention to a location in Texas and referred to as the Las Colinas Area Personal Transit System. 
     The system 10 includes a first guideway lane 12 which extends from a maintenance building 14 to a Government Center Station 16 through various other stations to a Xerox Center Station which is currently the last station on the guideway lane. 
     A second guideway lane 20 extends from the station 16 to a Las Colinas Boulevard Station 22. Normally, where guideway lanes are placed beside each other along a common run, it is desirable that the lane spacing be minimized consistent with operating requirements because of construction and land costs. Once the lane spacing is defined, it is highly desirable that any guideway switches needed for lane switching be structured so that they can be located within the available lane space without requiring costly widening of the lane spacing around the switch locations. In the present case, the spacing between lane centerlines is 11 feet. 
     Dotted guideways 24, 26, 28, and 30 represent planned future guideway additions. Various additional stations are provided for the guideways as indicated by the illustrated blocks with accompanying station names. 
     In the present system configuration, right hand single turnout guideway switches 32 and 34, as well as a planned future left hand single turnout switch 35, are located near the Maintenance Building. A double turnout guideway switch 36 is also located nearest the Maintenance Building and two double turnout guideway switches 38 and 40 are located near the Caltex station. 
     Guideway switches 42 and 44 provide a crossover between the lanes 12 and 20 of a dual guideway. The crossover guideway switches 42 and 44 are right hand single turnout switches which provide the lane crossover routing without requiring widening of the specified guideway lane spacing. Use of transfer tables, pivotal switches and other prior art schemes would require lane widening for switch placement. 
     GUIDEWAY CONFIGURATION 
     The guideway configuration is illustrated in FIG. 1B by means of a cross-sectional view of the elevated guideway with a vehicle on it. FIG. 1C shows the guideway configuration at a guideway switch location. Generally, the guideway can be structured so that the vehicle tire running surfaces are above or below or at ground level. A vehicle 58 is provided with rubber tires 60 that propel the vehicle 58 when running vertically on surfaces 50 and 52. 
     As shown, the guideway tire running surfaces 50 and 52 can be spaced surface portions running along the length of the surface of an elongated concrete guideway slab 54. In this case, it is preferred that the running surfaces be provided on pads 55 elongated in the longitudinal direction and extending slightly upwardly from the concrete guideway structural slab 54. Cable troughs 162 and 164 are respectively provide outwardly of the tire running pads. Metallic covers 161 and 163 are provided for the troughs 162 and 164. If the vehicle should become disabled and stop at any point along the guideway, the surface of the cover 161 and the tire pad surface 50 together and the surface of the cover 163 and the pad tire surface 152 together form respective sidewalks for passenger use. 
     A guidebeam 56 is supported by the slab 54 and extends along the slab 54 midway between the running surfaces 50 and 52. The vehicle 58 carries guide wheels 62 and 64 having rubber tires that run horizontally along the guidebeam structure provided by successive guideway slabs to provide lane guidance for the vehicle 58. 
     Electric rail structure runs along the length of the guideway slab and is supported above and to one side of each of the running surfaces. Generally, the rail structure is configured to provide electric power for vehicle propulsion and electric signals for vehicle control. 
     Specifically, rails 66, 68 and 70 carry power current for the vehicle 58 and rails 72 and 74 carry central station control signals for directing vehicle operation on the guideway. 
     In the preferred guideway configuration, the electric rail and guidebeam structure is located above and between the vehicle tire paths and it is organized to enable continuous current collection through continuous electric railing at guideway switch locations without mechanical on/off rail ramping of &amp;he car collector assemblies. By this location definition it is meant that the current collection surfaces on the electric rails and the guidance surface on the guidebeam are located above and between the tire surfaces. Normally most or all of the guidebeam and electric rail structure would thus be above the reference plane through the tire paths, but some portions of this structure may be located below the tire path reference plane so long as the current collection and guidance surfaces are located above this reference plane and between the tire paths. Current collection and guidance hardware on the underside of the vehicle can thus be designed to provide: 1) specified ground clearance for the underside of the vehicle; 2) in conjunction with the rail structure, completely reversible vehicle operation on the guideway; and 3) in conjunction with the rail structure, continuous current collection through guideway switch locations without mechanical on/off rail ramping of the vehicle collector assemblies. 
     Further, the running surface, electric rail and guidebeam structure is preferably symmetrically disposed on the two sides of the guideway lane centerline thereby enabling turnaround operation of vehicles on the guideway. By turnaround operation, it is meant that either end of the vehicle can be the leading vehicle end for vehicle travel over a guideway lane in either guideway direction with guidance and current collection functions being provided in both directions of vehicle travel. Generally, turnaround operation is enabled by the described symmetric disposition of electric rail and guidebeam structure and cooperative placement of guidewheel and collector assemblies on the underside of the vehicle. 
     For more information on the background, functions and advantages of the illustrated guideway configuration, reference is made to the cross-referenced copending U.S. Pat. application Ser. No. (54,460). 
     SINGLE TURNOUT ROTARY GUIDEWAY SWITCH 
     A single turnout rotary guideway switch 100 FIGS. 2A-2C) is arranged to provide for vehicle turnout from a main guideway lane to a turnout lane. 
     In one rotary position referred to as the tangent rotary position, the upper side of the guideway switch 100 provides a guideway configuration (guideway, guidebeam, and rail structure) that keeps the vehicle in the lane in which it is moving. When the guideway switch 100 is rotated, preferably through 180 degrees, the previous lower side of the guideway switch 100 becomes the upper switch side and it provides a guideway configuration that directs the vehicle from the lane in which it enters the switch (1) over a turnout path on the switch to a turnout lane or, alternatively, (2) over a crossover path to the other lane of a dual lane guideway. In the later case, the crossover path leads to another rotary guideway switch 100 located in the other lane and rotatively positioned to direct the vehicle onto the other lane. 
     Generally, the rotary guideway switch 100 is structured to expose the vehicle as it moves through the switch 100 to a guideway cross-section that is essentially the same as that which exists elsewhere along the guideway. Electrical contact with power and signal rails is continuous as the vehicle moves through the guideway switch 100 in either guideway switch position. 
     Crossover on a dual lane guideway is achieved without requiring that normal guideway spacing be increased or bulged to permit guideway switch installation. Normally, the spacing of dual guideway lanes is made as small as possible to economize on land and construction costs without sacrificing safety, operational and aesthetic requirements. 
     Further, as will become more evident hereinafter, self-aligning, failsafe operation of the rotary guideway switch 100 results where the weight of the vehicle load and the switch itself maintain the switch in its existing rotational position. System safety is thereby significantly enhanced. 
     Preferably, only one of the two guideway tire paths is provided on the tangent side of the switch frame 110. The substantial equivalent of one guideway path (i.e. a portion of each of the two tire paths that together substantially correspond to one path) is preferably provided on the turnout side of the switch frame 110. In this manner, the different guideway configurations required for the two different guideway switch positions can be provided with significant reduction in the switch load bearing requirements and in the switch weight and thus with significant economy and efficiency in switch design and operation. 
     In end effect, the described &#34;single tire path&#34; structure is a key to providing a minimum weight for a movable section of the guideway while meeting switching requirements. Thus, the same guideway configuration found outside the rotary switch is essentially duplicated by the switch section in both switch positions through rotation of the described rotatable switch element 110 without requiring rotation of the entire guideway cross-section. 
     The rotary guideway switch 100 is characterized with design flexibility especially since it is readily adaptable to meeting a variety of path switching needs. Among other benefits, its design flexibility additionally facilitates the development of switch designs for different radii of curvature specifications. 
     There is shown in FIG. 2A a section of a guideway having the single turnout rotary guideway switch 100 in its tangent position. Accordingly, a vehicle is guided over tire running surfaces 102 and 104A, 104B along a main lane 106 as opposed to being switched onto turnout lane 108. 
     The rotary guideway switch 100 comprises a rotatable and in this case generally rectangular frame member 110 that is supported in a switch pit 112 (FIG. 2C) for rotation about longitudinal centerline 112C. Hydraulic and electric operating equipment is also housed in the pit 112 at opposite ends of the frame member 110. Generally, switching is achieved by a hydraulic actuator that rotates the movable frame 110 through 180 degrees about a longitudinal axis from one of its aligned positions to its other aligned position. The switch is secured in either aligned position, preferably by four hydraulically actuated lock pins. More detail is presented subsequently herein on the switch operation. 
     The main guideway has longitudinally extending outer housing walls 116 and 118 within which the tire running surfaces 102 and 104A, 104B, guidebeam 120A, 120B, and power and signal rails 122A and 124B are provided. The tire pad with its surface 102 is included as part of the fixed guideway structure. 
     In the tangent switch position illustrated in FIG. 2A, the upper side of the guideway switch 100 is the tangent side which provides a tire running surface section 104SM (FIG. 2C) that connects main lane tire running surface 104A with main lane tire running surface 104B for continued main lane vehicle operation. A guidebeam section 120SM on the switch movable element 110 connects guidebeam 120A to guidebeam 120B to keep the vehicle on the main lane 106 as it passes through the switch mowable element 110. Power and signal rail sections 122A, 122B and 124A, 124B similarly provide main lane interconnections for continuous main lane vehicle electrical contact. 
     As shown in the cross-sectional view in FIG. 1C, horizontal guide wheels 126 ant 128 guide the vehicle over the guideway along the guidebeam 120, in this case the switch guidebeam section 120SM. Electrically conductive brushes on the vehicle provide circuit continuity with the electrical rail sections 122SMA, 122SMB, 122SMC, 122SMG, and 124SMS as the vehicle moves through the guideway switch 100. 
     In the turnout switch position illustrated in FIG. 2B, the guideway switch 100 is rotated so that the lower or turnout side of the switch element 110 in FIG. 2A becomes the upper side of the switch 100 in FIG. 2B. The turnout side of the switch 100 provides a tire running surface section 102ST and a short section 104ST that respectively connect tire running surface 102A and 104A on the main lane 106 with tire running surface 102C and 104C on the turnout lane 108 for vehicle turnout operation. A guidebeam section 120ST on the switch element 116 connects guidebeam 120A to guidebeam 120C to provide vehicle turnout guidance as the vehicle passes through the guideway switch 100. Power and signal rail sections 122C and 124C similarly provide connections for vehicle turnout operation (FIG. 2C). 
     With main lane operation, the tire running surface 102 is on a pad that is part of the fixed guideway structure and the other tire running surface 104 includes the switch tire running surface 104SM. When the guideway switch element 110 is rotated to its other position, the main lane tire running surfaces 102A and 104A are coupled to turnout lane tire running surfaces 102C and 104C by the respective switch tire running surfaces 102ST and 104ST. Significant weight savings and size savings (i.e. radius of rotation) are thus achieved for the rotary guideway switch 100 thereby providing economy of switch manufacture and facilitated switch operation. Significant failsafe switch operation results from the fact that the vehicle weight always acts on the switch tire surface 104SM in the high speed main lane switch position to hold the switch element 110 in position against its safety stops even in the highly unlikely event that all lock pins should be in the unlocked position. 
     In the lower vehicle speed turnout switch position of this single turnout embodiment of the invention, the vehicle weight similarly acts to provide lock pin backup over a substantial part of the length of the switch element 110. As will become more evident hereinafter, switch geometry is or can be arranged in various embodiments of the invention to enable complete backup protection through vehicle weight action. 
     To provide protection against wrongful vehicle entry into a switch that: is not aligned with the vehicle switch entry path, i.e. a switch aligned with the other guideway switch entry path, guide wheel stops are provided at the frog end of the switch. In FIG. 2A, stop 130 prevents a vehicle on turnout from entering from the frog end of the switch. In FIG. 2B, stop 132 prevents a vehicle on the main lane from entering from the frog end of the switch. 
     SINGLE TURNOUT - SWITCH AND EQUIPMENT LOCATION 
     In FIG. 2C, the single turnout rotary guideway switch 100 is shown with more detail that highlights the location of various structural and equipment items. The switch 100 includes a rotatable frame, a pit for the frame, and other fixed components. The switch pit 112 is an elongated cavity located within the guideway structure to house the generally elongated rotary guideway switch 100 for rotation and to house the equipment and structure needed to drive and support the guideway switch 100. Thus, the pit 112 is roughly subdivided into a main pit (31.5 feet long in this embodiment), a frog end equipment pit (4 feet long) and a point end equipment pit (4 feet long). 
     The switch rotation occurs about longitudinal centerline 112C. In moving from the tangent position shown in FIG. 2C to the turnout position, the guideway switch 100 rotates in the clockwise direction about the centerline 112C as viewed from the left side of FIG. 2C. As previously considered, the tangent side of the switch 100 provides tire running surface and guidebeam and electrical rail structure appropriate to main lane routing. The turnout side of the switch 100 is appropriately configured for turnout routing. 
     A fixed or frog end 140 of the guideway switch 100 is supported by a drive shaft 142 and lock pins 144 and 146. Pit space 113 is provided adjacent to the frog end 140 of the switch 100 to house electrohydraulic equipment 147 that drives the frog end switch shaft 142 for switch rotation and operates the frog end lock pins 144 and 146. 
     A fixed equipment frame 149 supports the drive shaft 142 and the lock pins 144 and 146. The fixed equipment frame 149 additionally includes a rotation safety stop 157A (FIG. 4) that provides backup engagement with a movable switch frame 110 of the switch 100 in its main lane position, i.e. the position shown in FIG. 2C. The inserted lockpins provide the primary definition of the main lane switch position, and the backup stop 157A (FIG. 4) secondarily defines the main lane switch position in the event the lockpins 144 and 146 are unlocked for some reason. Thus, in the higher speed main lane switch position, vehicle weight is applied over the entire path of vehicle travel against the movable switch frame 110 always to force the switch frame to rotate toward the fixed frame stop 157A. As subsequently considered more fully, the rotary frame weight distribution also causes the switch frame 110 to rotate toward the stop 157A. 
     A point or expansion end 148 of the guideway switch 100 is supported by a shaft 150 and lock pins 152 and 154. Another fixed equipment frame 153 supports the shaft 150 and the lock pins 152 and 154. The frame 153 also supports electrohydraulic equipment 155 for operating the point end lock pins 152 and 154. 
     The fixed equipment frame 153 also includes a rotation safety stop 157 (see FIG. 6 series) that engages a switch frame portion as a backup for the switch 100 in its turnout position. The stop 157 thus secondarily defines the turnout position of the switch element 110, with the primary turnout position definition provided by the lockpins 152 and 154 when they are inserted into the switch element 110. If all of the switch lock pins are unlocked for some reason in this embodiment, the stop 157 acts as a backup support for the switch frame 110 in its turnout position during the portion of vehicle travel over the switch 100 when the vehicle weight and the switch frame weight urges the switch toward the fixed frame stop 157. 
     The single turnout switch frame structure can be basically organized like the double turnout switch structure subsequently described herein to adjust the interface between the fixed structure tire path and switch tire path such that the switch tire path geometry enables the vehicle weight to push the switch against its turnout position stop over the entire switch tire path. In that case, continuous and complete backup rotation stop support is also provided in the turnout position of the single turnout switch. 
     A switch logic cabinet 156 and a hydraulic unit 158 are located outside the guideway structure to provide for guideway switch control and operation. A control conduit 160C and hydraulic lines 160H are routed through the guideway concrete structure for connection to the electrohydraulic equipment 147 and 155. Cable troughs 162 and 164 are provided for routing system signal lines along the entire length of the guideway, and, as shown, the troughs can also be used to route the electrical and hydraulic lines 160C and 160H locally from one end of the pit 112 to the other pit end. 
     To assure smoothness in the vehicle ride while providing more than adequate space tolerance for switch rotation, the spacing between each end of switch 100 and the adjacent fixed equipment frame 149 or 153 is preferably nominally 1/2 inch. Moreover, in constructing the guideway system, the equipment frames are secured in place with tolerances that assure placement of the rotary switch 100 such that its upper side configuration in either rotational position is in configuration alignment with the adjacent fixed guideway structure. 
     FIGS. 3 and 3A-3P2 show various views of the guideway structure with the switch element 110, point end frame 153 and frog end frame 149 removed from the pit 112. The pit geometry and the way in which the switch 100 fits in the pit 112 can thus be better perceived from these Figures. Some noteworthy aspects of the structure Will be described. Reference characters used in connection with FIG. 2C have been applied to FIGS. 3-3H, 3J-3N and 3P as appropriate. As indicated, this particular embodiment specifically applies to a right hand turnout switch having a 75 foot radius of curvature. Centerline designations in the various views are as follows: TP means tire path; RF means rotation and foundation; and ML means main lane. 
     As previously indicated, the tire path 102 on the main lane 106 is formed fixed wall structure including path portion 102 which runs along one of the longitudinal sides of the pit 112. When the rotary guideway switch 100 is in place in the pit 112 (FIG. 2C), one of the longitudinal sides of the switch 100 is disposed adjacently along the main lane path portion 102. 
     For a vehicle entry at point end 172 (FIGS. 2C and 3) of the guideway switch 100, fixed main lane path portion 102A is continuous with the fixed tire path portion 170 along the main lane tire path 102. However, fixed main lane tire path portion 104A is interfaced with the rotary switch element 110 by mean&#39;s of a tread plate 178. Similarly, at vehicle exit (frog) end 173 of the guideway switch 100, main lane tire path portions 102 and 102B are continuous. A tread plate 180 interfaces the switch tire running surface on either side of the rotary switch with main lane tire path portion 104B or turnout tire path 102C according to the rotational position of the guideway switch element 110. 
     The frog end equipment frame is supported by pillasters 190 and 192. As shown in FIG. 3B, the pit is structured also to provide support for the tread plate 180. Similarly, pillasters 194 and 196 provide support for the point end equipment frame and the tread plate 178. 
     As shown in FIGS. 3A and 3B, the floor of the pit 112 is sloped to provide for drainage through a drain 191. Alternate pit structures, elevated or at grade, may not have floors and would use standard structural steel shapes (e.g. I-beam) for primary members. 
     The FIG. 3 series of sectional views highlight various structural features of the rotary switch pit 112. FIGS. 3A and 3B show the longitudinal sides of the pit 112 in elevation from the inside of the pit 112. FIGS. 3C-L show various pit elevational cross-sections that highlight the wall and pillaster structure for tread plate and equipment frame support. FIG. 3M1 and 3M2 are sectional views of the frame 153 secured to the pilaster 194 and accordingly provide additional perspective for this structure. FIGS. 3N1-3P2 are details of plates 178 and 180. These detail views are similar to detail views considered more fully subsequently herein in connection with the crossover switch embodiment of the invention. 
     SINGLE TURNOUT SWITCH-FRAME STRUCTURE AND SWITCH ASSEMBLY 
     In FIG. 4, the tangent or main lane side of the single turnout rotary guideway switch rotating frame 110 is shown in a plan view. The basic structure of the switch 100 formed by a generally elongated structural frame member 110 comprising parallel longitudinal structural I beams 202 and 204 and frog end, point end and center cross I beams 206, 208 and 210. 
     From a strength standpoint, the switch framework is arranged to meet all structural and vehicular induced loads within tolerable bending and torsional stresses and specified maximum deflection. From an electrical standpoint, the switch is structured to provide power and signal rail continuity for a vehicle as it enters, passes through and exits the switch. 
     Generally, the length of the frame 110 is based on the specified radius of curvature for the turnout path at the switching area. A greater radius of curvature requires a greater switch length. In this case, the switch length is approximately thirty-one feet. 
     The width of the switch frame 110 is preferably less than the overall distance between the tire paths, but the frame width is sufficient to provide the necessary interface width of turnout guideway path on the turnout side of the switch 100 (with the main lane tire path fixed on the side opposite the turnout side). In this way, the rotary switch 100 can be structurally designed with economy for partial car loading as opposed to full car loading. Further, the weight of the rotary ewitch itself is limited and the rotational diameter of the rotary switch 100 is limited thereby enabling economy in the switch and guideway pit structure and facilitating the operation of the rotary switch 100. In particular, the relatively small size and weight of the switch rotating frame 110 produces efficiency allowing low operational horsepower requirements (less than two horsepower in this application). 
     The switch frame width in this embodiment is such that the longitudinal beam 202 provides a tire path on the main lane side of the switch 100 for the tires on one side of the vehicle, and the longitudinal beam 204 is placed to lie just inside and below the fixed structure path (see FIG. 3) for the tires on the other side of the vehicle. Thus, only half of the vehicle weight is carried by the rotary switch frame 110 and its support structure in the main lane position. 
     As in the present case, the rotary switch frame length can be great enough in relation to the vehicle length that a portion of a second vehicle connected to the first vehicle may be located on the rotary switch frame 110 while the entire length of the first vehicle is on the switch frame 110. In that case, the rotary switch frame 110 is designed to support one half of the total vehicle weight that can bear on the main lane side of the rotary switch frame, i.e. the portion of the weight of the full first vehicle translated through the vehicle tires on one side of the vehicle and the portion of the weight of the connected vehicle translated through the single vehicle tire located on the rotary switch frame 110. 
     On its main lane side, the frame 110 is additionally provided with the main lane guidebeam section 120SM which is secured to the cross beams 206, 208, and 210. The power and signal rail structure is not shown in FIG. 4. 
     A curved beam 212 provides cross frame support in the diagonal direction between the longitudinal beams 202 and 204 such that it provides the turnout tire running surface 102ST on the turnout side of the rotary switch 100 (the underside of the frame 110 as viewed in FIG. 4). For structural purposes, a bracing I-beam 214 provides similar cross frame support in the opposite diagonal direction, The curved turnout guidebeam section 120ST is also provided on the switch turnout side. 
     Preferably, fiberglass grating is incorporated into the rotary switch frame to eliminate open areas between structural members and thereby facilitate maintenance and provide a secure stepping surface for passengers who may have to leave a vehicle that has had an emergency stop in the vicinity of a switch. Since the upper and lower sides of the switch frame are used for vehicle routing, the grating is installed to provide for loading on either side of the grating surface. Thus, the grating supports take loading in both directions. 
     Rotational backup stop action is provided at opposite ends of the switch framework. As indicated by dotted lines in the upper left hand corner of FIG. 4 (detail in FIGS. 9B1-9B2), the safety stop 157A is a stop secured to the frog end fixed equipment frame 149 and is structured and positioned such that its top surface provides stop support, and preferably backup stop support, for the underside of corner portion of top plate of the longitudinal I beam 202 of the frame 110. 
     Just prior to reaching the main lane stop position, the switch frame 110 is brought to a smooth stop in alignment for insertion of the primary frame supporting lock pins. The described stop structure acts as a backup support in the event lock pins fail to be inserted, i.e. the weight of the switch itself and any vehicle load pushes the switch frame a slight (less than 1/16&#34;) additional distance against the backup stop structure. 
     To enable the switch frame 110 to rotate into the main lane position shown in FIG. 4, the bottom plate of the longitudinal I beam 202 of the frame 110 is notched to remove its corner portion that would otherwise contact the frog end stop 157A and prevent the switch frame 110 from being rotated fully into its main lane position. 
     As shown in the upper right hand corner of FIG. 4, a safety stop 157D is also preferably provided on the point end of the rotary switch. In this instance, the stop 157D is secured to the rotary frame and it has a projecting finger that engages a stop structure 157B (detail in FIGS. 9A1-9A2) on the point end fixed frame 153 if lockpin support fails in the illustrated main lane position. 
     In the turnout position of the switch, the bottom surface of the frog end stop 157A similarly provides backup support for the inner surface (upwardly facing in the switch turnout position) of the abutting corner portion of the bottom (in turnout position) flange of the I beam 204. The opposite (top) flange of the I beam 204 is notched as indicated by 157E so that it can pass the stop 157A as the switch frame rotates into its turnout position. The point end stop structure 157C on the point end fixed frame 153 likewise provides backup support in the turnout position for frame stop structure 157D. 
     Support structures for the frog end drive shaft 142 and the point end shaft 150 are shown respectively in FIGS. 4A and 4B. 
     As shown, the drive shaft 142 is supported relative to the fixed ipment frame 149 by means of a fixed tapered roller bearing assembly 216 on which the switch frame is rotated. The tapered roller bearing assembly is a long-life, anti-friction unit that provides smooth operation and includes the following elements: 
     218 pillow block and grease fitting 
     220 bearing cone and bearing cup 
     222 bearing seal 
     224 seal retainer and gasket 
     226 bearing sleeve 
     228 screw 
     230 lock washer 
     232 locknut 
     The point end shaft 150 is supported relative to the fixed equipment frame 153 by means of another fixed tapered roller bearing assembly 234 on which the switch frame is rotated. As above, the tapered roller bearing assembly 234 includes the following elements: 
     236 pillow block and grease fitting 
     238 bearing cone and bearing cup 
     240 bearing seal 
     242 seal retainer and gasket 
     244 bearing sleeve 
     246 screw 
     248 lock washer 
     250 locknut 
     The two switch frame shafts 142 and 150 are respectively supported relative to the switch frame cross beams 206 and 208 by similar spherical bearing assemblies 251 and 253 which accordingly provide structural bearing for the switch frame. Each of the spherical bearing assemblies 251 and 253 includes the following elements: 
     255 spherical bearing supported on shaft 
     257 bearing seat 
     259 lock washer 
     261 locknut 
     A crankarm 263 is provided with the bearing with the assembly 251 and another crankarm 265 is provided bearing assembly 253. Each crank arm 263 or 265 is secured to its shaft 142 or 150 and extends radially outwardly to a point where it has an end portion coupled to the switch frame cross beam 206 or 208. Accordingly, when the crank arm 263 (see the FIG. 5 series) is driven by the shaft 142, it provides rotational drive force for the switch frame 110. The crank arm 265 similarly connects the passive point end shaft 150 and frame end beam 208 for coupled movement. While the point end crank arm 265 transmits no drive force to the switch frame because the point end shaft 150 is free to rotate, it does tie the frame movement to the movement of the point end shaft 150 so that point end shaft position can be used to confirm the frame point end position with the frame frog end position with use of a position detection device. 
     The frog end bearing assembly 251 includes spacers 267 and 269 which fix the bearing 257 and the shaft 142 against relative movement in the axial direction. Thus, the frog end of the switch frame is fixed against movement in the longitudinal direction which could otherwise occur as a result of thermal expansion and contraction of the switch frame 110 or as a result of frame bending under vehicle load or vehicle braking or acceleration forces. 
     At the point end of the frame 110, spacers like the spacers 267 and 269 are omitted thereby enabling the frame point end to undergo longitudinal movement under thermal or vehicle load. In the illustrated embodiment, space is provided for about 3/8 inch outward (rightward) or longitudinal frame movement due to thermal expansion whereas the expected maximum outward movement is 1/4 inch. As indicated by reference character 209, space is provided for about 1 inch inward (leftward) longitudinal frame movement due frame bending under vehicle load or due to thermal contraction or installation tolerances. 
     FIGS. 4C and 4D show enlarged views of the frog end cross beam 206 for the guideway switch frame 110. The point end cross beam 208 is the same as the beam 206. 
     As shown in the elevational view of FIG. 4C, the end beam 206 has respective seats 191 and 193 having openings 195 and 197 for receiving lock pins when the rotary switch frame 110 is rotated into either of its two guideway operation positions. As shown in the plan view having portions broken away (FIG. 4D), lock pin support is provided by a spherical bearing 199 or 201 which is provided with a retaining ring 2C3 or 205 and a grease fitting 207 or 209. 
     At a central location of the rotary frame end beam 206, the bearing seat is provided with an opening 221 for receiving the frog end drive shaft 142. The spherical bearing 255 provides shaft support. A retaining ring 215 and a grease fitting 217 are again provided for the bearing 255. 
     To provide for switch frame rotation, the end beam 206 additionally has a seat 211 with an opening 223 for receiving the radially outward end of the crankarm 263 which is connected to the frog end drive shaft 142. A spherical bearing 225 supports the crankarm 263. Again, a retaining ring 227 and a grease fitting 229 are provided for the bearing 225. 
     The preferred shaft support arrangement for the switch frame 110 is a type of load support structure referred to as a Simple Supported Beam. 
     The lockpins and rotating shaft are mounted on spherical seats located on a common reference line thereby freeing the framework to rotate about the center line as a hinge line under induced vehicle load. With hinge line rotation, translational forces to the hinge line are always vertical, and moments are distributed along the switch framework while essentially no bending moments are induced on the lockpins and shafts, i.e. the latter are significantly reduced in size compared to fixed end support (such as straight bore as opposed to spherical bearing receptacle). In effect, the switch frame carries vehicle load and transfers minimal bending moments to the supporting shafts and lockpins without frame leveraging that would otherwise cause high stresses on the shafts and lockpins. 
     The hinge line is designated by the reference character 256F in FIG. 4 at the frog end and is best observed in FIG. 4A. A. similar hinge line 256P operates at the point end of the frame, and it is best observed in FIG. 4B. 
     As a result of the operation of the preferred simple support structure for the switch frame support arrangement, vehicle load forces are transmitted through the frame hinge lines essentially as shear stress on the shafts and the lock pins. Otherwise. bending loads applied over the length of the switch frame would produce high tensile stresses on the shafts and locking pins thereby requiring excessively or impractically sized structures for these supporting elements. 
     It is also significant that the described spherical bearing support structure provides a self-aligning feature permitting 180° rotation of this switch frame 110 without binding against the shafts due to thermal distortion or due to manufacture to accuracy limitations. This self-alignment occurs since the spherical bearings can rotate relative to the switch frame. 
     Preferably, the lock pin spherical bearings have extended rings that limit the extent of bearing rotation relative to the switch frame thereby assuring alignment conditions for lock pin insertion, to line up with centerlines of the frame support shafts. The lock pin spherical bearings similarly provide self-alignment since the bearings can rotate relative to the switch frame to permit lock pin alignment with the bearings when the switch is rotated into position for lock pin insertion. 
     In a particular commercial embodiment, the framework was formed from A36 steel employing both rolled and fabricated structural sections. The framework had a span of 31 feet 3 inches, a depth of 17 inches and a width of 6 feet 7 and 1/4 inches. To minimize the cumulative effects of fatigue, all connections except one were secured by high strength bolts. Maximum give load deflection at midspan was 1/4 inch. 
     The assembly of the rotary switch frame 110 with the fixed equipment frames 149 and 153 is shown most clearly in FIG. 5. This Figure is similar to FIG. 3 but it is slightly enlarged and it highlights more assembly detail. FIGS. 5A through 5E show views taken along the indicated reference planes and are further enlarged to provide a better showing of various features of the structural assembly. 
     As shown in FIG. 5, the drive shaft 142 is driven by a rotary hydraulic actuator 300 of the piston driven rack and pinion type. In the referenced commercial embodiment, the rotary actuator had a maximum torque of 30,000 in. lbs. with system relief maintained at a pressure of 1200 psi. Maximum working capacity is 75,000 in. lbs. at 3000 psi. 
     Point end lock pins 302 and 304 are respectively driven by hydraulic actuators 306 and 308. Similarly, frog end hydraulic actuators 310 and 312 respectively drive point end lock pins 314 and 316. The actuators have built-in cushions for end-of-stroke deceleration. 
     FIG. 5A shows the fixed equipment frame 153 from the point end and toward the rotary switch frame. Accordingly, the spatial relationship of the passive shaft 150 and the lockpins 304 and 302 is clearly illustrated. 
     FIG. 5B is an enlarged view that shows the frog end lockpin and rotary shaft actuators in elevation from the frog end of the rotary switch frame. FIG. 5C is an enlarged view showing the relationship of the rotary actuator 300 to the drive shaft 142. 
     FIG. 5D is an enlarged view that shows the lockpin system with the lockpin 3C2 in the locked position. When the lockpin is moved to its unlocked position by the actuator 306, pin end face 307 is moved rightward so that it is located within bearing block 319 which is supported by the fixed frame 153. FIG. 5E is similar to FIG. 5D except that it pertains to an inactive switch, i.e. a switch that is installed to provide guideway operation in one lane with the expectation that the switch will be usable at a later date when another lane to which it is to be connected becomes operational. Accordingly, the lockpin is held in a fixed locked position by the structure located to its right in FIG. 5E. 
     As an additional advantage, the maintenance requirements are relatively minimal because of the simplicity of design and operation of the rotary switch. Thus, the spherical, sleeve and tapered roller bearings supporting the switch shafts and the lockpins can be selected for high capacity with extended life and minimal maintenance. Readily accessible grease fittings are preferably used to facilitate periodic lubrication. The lockpins, shafts, gear segments, and hardware associated with the lockpin actuating cylinders are preferably made from stainless steel to resist the detrimental effects of corrosion. Further, shafts are preferably oversized to assure product durability. 
     Respective position sensors (referred to in the trade as controllers) 318, 320, 322, and 324 are provided to generate feedback position signals for the lock pins 314, 316, 302 and 304. Gear driver: position sensors 315 and 317 are respectively coupled to the frame shafts 142 and 150 to provide feedback signals that define the rotary frame position. 
     The hydraulic actuator and sensor equipment items are supported on the respective frog end and point end fixed frames 149 and 153. The frog end fixed frame structure is shown in greater detail in FIGS. 6-1F, 6-2F, 6-3F, and 6AF through 6DF. The point end fixed frame structure is shown in greater detail in FIGS. 6-1P, 6-2P, 6-3P, and 6AP through 6FP. 
     The following table defines the structural elements of the two fixed frames: 
     EQUIPMENT FRAME (FROG END) 
     SINGLE TURNOUT GUIDEWAY SWITCH (RH) 
     
         ______________________________________                                    
Reference                                                                 
Character   Part Description                                              
______________________________________                                    
F1          Beam 6.75 wide × 8.0 high × .75 thick,            
            75.62 long                                                    
F2          I-BEAM W 6 × 16, 43.25 long                             
F3          I-BEAM W 6 × 16, 43.25 long                             
F4          I-BEAM W 6 × 16, 46.45 long                             
F5          PLATE 7.25 × 12.00 × .50                          
F6          PLATE 7.25 × 12.00 × .50                          
F7          ANGLE 3.0 × 3.0 × .375, 4.0 long                  
F8          CONTROLLER SUPPORT ASSEMBLY                                   
F9          CONTROLLER SUPPORT ASSEMBLY                                   
 F10        CONTROLLER SUPPORT ASSEMBLY                                   
 F11        CYLINDER SUPPORT                                              
 F12        CYLINDER SUPPORT                                              
 F13        GUSSET                                                        
______________________________________                                    
 
    
     EQUIPMENT FRAME (POINT END) 
     SINGLE TURNOUT GUIDEWAY SWITCH (RH) 
     
         ______________________________________                                    
Reference                                                                 
Character   Part Description                                              
______________________________________                                    
P1          Beam 6.75 wide × 8.0 high × .75 thick,            
            75.62 long                                                    
P2          I-BEAM W 6 × 16, 43.25 long                             
P3          I-BEAM W 6 × 16, 43.25 long                             
P4          I-BEAM W 6 × 16, 46.45 long                             
P5          PLATE 7.25 × 12.0 × .50                           
P6          PLATE 7.25 × 12.0 × 5.0                           
P7          ANGLE 3.0 × 3.0 × .375, 4.0 long                  
P8          CONTROLLER SUPPORT ASSEMBLY                                   
P9          CONTROLLER SUPPORT ASSEMBLY                                   
 P10        CONTROLLER SUPPORT ASSEMBLY                                   
 P11        CYLINDER SUPPORT                                              
 P12        CYLINDER SUPPORT                                              
 P13        GUSSET                                                        
______________________________________                                    
 
    
     ROTARY SWITCH--HYDRAULIC CONTROL SYSTEM 
     In FIG. 7, there is shown a schematic diagram for a hydraulic control system 400 that operates the rotary actuator and the lock pin actuators when the rotary guideway switch is to be moved from one position to its other position. Dotted box 402 encloses those elements of the system 400 that are contained in the hydraulic unit located outside the guideway and noted in connection with FIG. 2C. Basically, the hydraulic power unit includes an electric motor, a motor driven hydraulic pump, a hydraulic manual pump, a fluid reservoir, directional control valves, pressure gauge, pressure relief valve, check valves, a safety valve, fluid filters and a control panel. 
     Normally, a system pressure of 700 psi maximum is used for switch operation. Preferably, the directional control valve for the look pin actuators is spring biased so that the actuators extend the lock pins to the locked position upon any loss of solenoid power. 
     Fluid lines 404 and 406, preferably made from stainless steel, connect the hydraulic unit 400 to the lock pin actuators 306, 308, 310 and 312. The rotary drive shaft actuator 300 is operated by fluid lines 408 and 410 from the hydraulic unit 400. The fluid lines 404-410 extend from the hydraulic unit 400 through the guideway structure to the switch pit 112 as previously noted. 
     A pump unit 412 develops develops the fluid pressure needed to operate the actuators. Hand pump 413 provides pressure development in emergency and other situations. 
     Pressurized fluid passes through a filter 414 to a valve 416 for the lockpin actuators 306, 308, 310, and 312 and through valve 416A and a valve 418 for the rotary actuator 300. 
     The line 404 operates the actuators 306-312 to extend the cylinders and push the lock pins into locking position in the lineal bearing seats in the rotary frame end beams after the frame has stopped in either its main lane position or its turnout lane position. The line 406 operates the lock pin actuators to withdraw the lock pins from the rotary switch frame thereby permitting switch rotation. With lock pins inserted. a secure and accurate switch alignment is assured. 
     The rotary actuator 300 operates through its rack and pinion mechanism to turn the shaft 142 in the forward direction to the switch main lane position when the line 408 is activated. Activation of the line 410 drives the shaft 142 in the reverse direction to the switch turnout position. 
     In the present single turnout embodiment, any one of the lock pins is sufficient to support the switch frame against rotation under vehicle loading. Even if all lock pins are unlocked, switch self alignment occurs in the sense that vehicle loading continuously forces the single turnout rotary switch against its stop in the high speed main lane switch position. With appropriate single turnout frame design, the same can be tire for the slower speed turnout lane switch position. The double turnout switch subsequently described herein does provide self switch alignment in both switch positions. 
     A wayside logic control (not shown) receives feedback signals from the lockpin and shaft position sensors and coordinates with the hydraulic unit to develop command control signals for the lock pin and shaft valves 416, 416A and 418 when the rotary switch position is to be changed under system automatic or operator supervision. 
     Provision is also preferably made for rotary guideway switch operation by means of a manual pump 413 without electrical power. The manual pump develops the required hydraulic pressure and thereafter the control valves are manually shifted to operate the rotary guideway switch. 
     The following describes the sequence of operations for a tangent-to-turnout switching for the previously referenced commercial embodiment: 
     Initial conditions required are that all valve solenoids be de-energized, manual operation valve 413A be in closed position, rotary switch frame in tangent position, and lock pins in locked position. 
     1. 115 VAC, 60 Hz power is sent to the solenoid on the Lock Cylinder Control Valve (LCV, 416) to shift the pool. 
     2. Simultaneously, 115 VAC, 60 Hz power is sent to the solenoid rotary beam float unloader actuator Valve (BFUV 416A) to the shift spool. This blocks flow to the rotary actuator and pressure develops to retract lock pins through LCV valve. Also at the same time 480 VAC, 3, 60 Hz power is sent to the motor in pump unit 412 to develop fluid pressure. 
     3. Pressure developed causes the pilot to open four check valves (306A, 308A, 310A and 312A). Pressure on the rod side of piston on each lock cylinder (306, 308, 310 and 312) causes each piston to fully retract, moving the lock pins to the unlocked position. Pressure (at cylinders) to move pins should be less than 100 psi, with initial pressure to unseat as high as 200 psi. Time of motion is approximately 2.1 seconds and stroke distance is 7.0 inches with 5.0 GPM pump. 
     4. Power to the solenoid valve BFUV 416A is switched off and the spring shifts the spool as 115 VAC, 60 Hz power, is sent to solenoid RCV on the two solenoid position control valve 418 to shift the spool. 
     5. Fluid pressure is developed on one side of the piston in the rotary actuator cylinder 300, the opposite side of the cylinder is open to the drainline on the opposite side of the cylinder. The force developed on the pressured side causes the piston to move which drives a rack to rotate the switch frame to the opposite position. Pressure (at cylinder) to rotate the switch is approximately 300 psi after initial buildup at 700 psi. Time of motion is approximately 10.0 seconds and stroke distance is 10.47&#34;, as limited by the maximum stroke of the piston which engages a built-in cushion at end of the stroke. 
     6. Power to solenoid BFUV on valve 416A is switched back on and shifting the spool. Simultaneously, power to solenoid LCV on valve 416 is switched off and the spring shifts the spool simultaneously, permitting flow into the head side of the lock pin cylinders and moving the lock pins into the locking position. 
     7. Solenoid RCV is de-energized removing pressure from the rotary actuator 300 putting the unit in a free float position. 
     8. When all lock pins are fully seated in the locked position, all solenoids and the motor contactor coil is de-energized. 
     OVERVIEW--SWITCH OPERATION 
     In the operation of the people mover system, each rotary guideway switch position is specified over the ATO circuit according to the path to be followed by vehicles moving in the system. Switch positions, sensed as previously noted, are checked against specified positions and any required changes are sent as switching commands over the ATO system. Wayside interlocking logic detects any guideway switch that fails to be positioned and locked as commanded and initiates safety car stoppage until the problem is corrected. If necessary, manual switch operation can be executed by operation of the hydraulic unit at the guideway switch location. 
     At the guideway switch location, a switch position change is implemented by the following actions: 
     1. The lock pin hydraulic actuators withdraw the switch frame lock pins. 
     2. The lock pin position sensors verify the withdrawal of the lock pins. 
     3. The rotary hydraulic actuator turns the drive shaft until the switch frame has moved from its previous position to its new position. 
     4. The shaft position sensors verify the existence of the new switch frame position. 
     5. The lock pin hydraulic actuators insert the lock pins into the switch frame. 
     6. The lock pin position sensors verify the insertion of the lock pins. 
     Total time for executing a switching operation is typically 10 seconds. 
     When the rotary guideway switch is in the main lane position, vehicle loading forces the switch frame toward the stop structure in the main lane position. Safe operation thus occurs even if the lock pins have been withdrawn from the switch frame and not reinserted for some reason. 
     Switch manufacture is significantly economized and switch operation is significantly facilitated by the fact that the switch structural strength and weight can be safely and relatively reduced because: 
     1. Reduced vehicle loading results from structuring the rotary switch so that only those tires on one side of the vehicle, or the substantial equivalent thereof, can be on the guideway switch as the vehicle moves over the switch in either switch position. 
     2. Reduced frame, lock pin and shaft strength requirements result from the hinge line, simple support arrangement. 
     As previously indicated, significant savings in system construction costs and enhancement in system aesthetics are provided by avoidance of any requirement for guideway bulging at crossover switching locations. These advantages essentially result from the &#34;single&#34; tire path configuration of the rotary switch. 
     From the standpoint of product strength, vertical loads induced in the switch frame are transmitted through the lock pins to the lock pin guide blocks on the equipment frames to the support pillasters. In the referenced commercial embodiment, the weight of the switch frame itself is 16,500 lbs. 
     Vehicle load is induced on the switch frame through the vehicle tires. In the commercial embodiment, load was specified at 7500 lbs. per tire with an axle spacing of 14.5 feet and with at most three; tires on the rotary switch frame. Maximum lateral loads due to guide tires was 3000 lbs. resulting in 3000 lbs. lateral load and an additional 1000 lbs. vertical load per main axle. To accommodate vehicle braking and acceleration on the switch frame, each equipment support was sized to take in excess of 9600 lbs. longitudinal load. Overall, switch frame stiffness was employed to limit deflection to less than 1/4 inch in the tangent switch position and less than 1/8 inch in the turnout position at specified vehicle loading. Differential thermal expansions of concrete, steel, aluminum and rigid plastic also were reflected in the commercial rotary switch design. 
     From the standpoint of safety, the following summary comments apply: 
     1. The switch tends by its own weight to rotate into the closest alignment position against structural stops. 
     2. In the high speed tangent position, the vehicle tires are only on one side of the switch frame to hold the switch against the stops even if the lock pins are unlocked. 
     3. The lock pins are sized to be structurally redundant, i.e. four levels of switch support in addition to the support from the structural stops. 
     4. Vehicle wrong entry stops keep the vehicle locked onto the guideway. 
     5. Continuous power and signal rail through the switch eliminates vehicle speed restrictions often required with the use of guideway switches having mechanical on/off rail ramping. 
     DOUBLE TURNOUT ROTARY GUIDEWAY SWITCH 
     Another embodiment of the invention is shown in the top plan view of FIG. 8A. In this case, a generally elongated rotary guideway switch 700 provides vehicle guidance between a main lane 702 and a left turnout lane 706 or a right turnout lane 708 according to the switch position. The guideway switch 100 is thus referred to as a double turnout switch. In practice, vehicles may move in either direction across the switch 700, i.e. either into or out of the turnout lanes 706 and 708, according to the people mover system design. 
     The turnout lanes 706 and 708 in this preferred case are symmetrical about main lane centerline 710. Accordingly, the double turnout switch 700 and its pit 704 are also disposed in the lane intersection area symmetrically about the main lane centerline 710. 
     As indicated by tire paths 712 and 714, the double turnout rotary switch 700 is positioned to direct car travel from the main lane 702 to the right turnout lane 708 for vehicles moving out of the main lane 702. The tire path 712 includes main lane portion 712M and right turnout lane portion 712RT which are formed by fixed guideway structure, whereas the tire path 714 includes main lane portion 714M, switch portion 714SRT and right turnout lane portion 714RT. The upwardly facing. right turnout side of the switch 700 provides the right turnout switch tire path 714SRT as well as a right turnout guidebeam 716SRT and turnout power and signal rail structure 718SRT and 720SRT. Four rails are shown on both sides to illustrate all combinations of rail installations and associated clearance for the illustrated embodiment. 
     A similar but opposite guideway switching interface is provided by the left turnout side of the rotary switch 700 which is rotated into an upwardly facing position (not indicated in FIG. 8A) when the switch 700 rotated about its longitudinal centerline through 180 degrees. Thus, the main lane tire path 712M is connected to left turnout lane tire path 712LI by a left turnout tire path on the switch 700, while the other tire path is formed entirely by fixed structure portions 714M and 714LT. Guidebeam and electrical rail structure are also provided to complete the left turnout guideway configuration on the left turnout side of the switch 700. 
     As previously, the pit 704 is provided with a frog end 704F and a point end 704P. Frog and point end equipment frames 722F and 722P support frame 700F of the double turnout switch 700 in a manner like that described for the single turnout switch, i.e. by means of lock pins and shafts. 
     At the point end, switch supporting lock pins 724LP1 and 724LP2 are operated by hydraulic actuators 726 and 728 with lock pin positions sensed respectively by sensors 727 and 729. A sensor 730 detects the position of a switch supporting point end shaft (not visible in FIG. 8A - see 736P in FIG. 8D). 
     Switch supporting lock pins 724 LP3 and 724LP4 are operated at the frog end by hydraulic actuators 732 and 734 with lock pin positions sensed respectively by sensors 733 and 735. A frog end drive shaft 736F (FIG. 8D) supports the switch frame, is driven by rotary actuator 737 and its position is sensed by unit 738. 
     The point end of the pit 706 is similar to that described for the single turnout guideway switch. As a result of space limitations presented by the guideway structure at the frog end of the pit 704, the position sensors /33, 735 and 738 are located outside the pit 704 and suitable couplings are provided through the guideway wall structure to enable these units to function as required. 
     Equipment frames mounted in the frog and point end pits for the double turnout guideway switch are conceptually like the equipment frames described for the single turnout guideway switch, with some structural differences providing for different mounting requirements. Generally, the equipment frames in both cases are symmetric about the centerline of switch rotation which as previously noted is the same as the guideway centerline. 
     A hydraulic control unit 715 and a switch logic cabinet are preferable, disposed outside the guideway structure and between the turnout lanes 706 and 708. Hydraulic and electrical line connections are generally made as previously described for the single turnout switch. 
     In FIG. 8B, the double turnout guideway structure is shown with the double turnout rotary guideway switch element removed. Generally, the pit 704 is contoured to the shape of the elongated switch frame 750F Concrete pillasters 740, 742, 744 and 746 provide support for the equipment frames 722F and 722P. Structural walls are provided with cable troughs as shown. 
     FIG. 8BA shows the right turnout side of the pit 704. FIGS. 8BB through 8BF are taken along reference planes as indicated to show views similar to those presented for the other embodiments of the invention. 
     The general assembly of the double turnout rotary guideway switch frame with its supporting structure is highlighted in the top plan view of FIG. 8C. FIGS. 8CA through 8CG are taken along the indicated reference planes and show various equipment views similar to those described in connection with the single turnout guideway switch embodiment. 
     In FIG. 8D, a top plan view is shown for the right turnout side of a generally rectangularly shaped frame assembly 750 for the double turnout rotary guideway switch. Views taken along reference planes A--A and B--B highlight the preferred simple shaft support arrangement for guideway switches made in accordance with the invention. 
     As in the case of the single turnout switch embodiment, the frame 750 is made symmetrical about the axis of rotation except to the e&gt;tent that asymmetry is needed to meet requirements of guideway configuration and structural strength. Specifically, curved portion 756C of the turnout beam 756 is disposed relative to the axis of frame rotation such that its outwardly facing tire path surfaces form right and left switch turnout paths that are symmetric about the axis of frame rotation as the switch frame is rotated from one turnout position to the other turnout position. 
     The double turnout frame assembly 750 has respective end beams 752 and 754 supported by the shafts 736F and 736P. As previously, crankarms tie the switch shafts to the double turnout switch frame through frame end beams to transmit rotational drive force to the frame at the frog end and to provide position indication at the point end. 
     The frame support shafts extend through spherical bearings seated in the respective frame end beams 752 and 754. As in the case of the single turnout switch embodiment, frame deflection occurs rotationally about respective end hinge lines passing through the lock pin seats and the frame shaft seats in the respective switch frame end beams. 
     Beam structure including a turnout beam 756 extends longitudinally and ties the end beams 752 and 754 together to form the basic structure of the frame assembly 750. 
     More structural detail is presented for the frame assembly 750 in the top plan view shown in FIG. 10E and in FIGS. 8EA-8EH which are taken along the respective designated reference planes of FIG. 8E. The right turnout side of the switch frame assembly 750 is seen in FIG. 10E, with the left turnout side of the switch frame 750 being located on the underside of the view. 
     Generally, the previously noted turnout beam 756 and an another elongated beam 75 form the longitudinal sides of the frame 750 and together provide the beam structure that tie the end beams together in forming the basic frame structure. The side beam 758 has less height than the turnout beam 756 since the turnout beam 756 is relatively elevated to provide turnout running surfaces for tires on one side of any vehicle that runs over the guideway switch for either a right or a left turnout. 
     The turnout beam 756 has the curved portion 756C which defines the turnout tire path on both sides of the switch frame 750. A side branch 756B of the turnout beam 756 extends to and secures to an end portion 757 of the frog end beam 736F thereby providing outer frame structure in the frame area where the curved beam portion 756C is located. Additional cross beams 759, 760 and 762 and diagonal beam 763 complete the frame structure 750. 
     The shaded path shown in FIG. 8E is the portion of top plate 766T that forms the right turnout tire path. 
     As observed best in FIG. 8EC, right turnout tire running surface 764R on right turnout side 750R of the switch frame 750 and left turnout tire running surface 764L on left turnout side of the switch frame 750 are in vertical alignment and are formed respectively by top and bottom plates 766T and 766B (FIG. 8EE) cf the tunnout beam 756. 
     To make the turnout beam 756, it is preferred that the top and bottom plates 766I and 766B be configured with the generally Y-shape observed in FIG. 8E and formed into beam structure by means of intersecured elongated web members 758 and 770 and cross web members 772-1 through 772™9 (FIG. 8EC). In this case, the curved beam portion 756C is formed as described to the point where it meets the cross beam 759. At that point, the curved beam 756C is &#34;continued&#34; to the frog end beam; 736F by the use of aligned top and bottom bridge plates 756T and 756B (FIG. 8EB). 
     Guidebeam structure is provided for the right turnout side 750R of the switch frame 750 by a curved guide beam 771R that is secured to the side beam 758 (FIGS. 8E and 8EA) and to cross beams 760 and 762 and point end beam 736P (FIG. 8E). A like curved guidebeam 771L (FIG. 8EA) is provided on the left turnout side 750L of the switch frame 750 in vertical alignment with the guidebeam 770R. 
     Electrical rails (not shown) for the double turnout guideway switch are like those described for the single turnout guideway switch. They are secured to the frame 750 by means of brackets 780 and 782 which are detailed in FIGS. 8EN-8ES. 
     The rotational backup stop structure for the switch frame 750 rotation is detailed in FIGS. 8CA, 8CB and 8EJ-8EM. As shown on the point end in FIG. 8CA, a stop structure 740P is secured to the point end fixed equipment frame and is positioned to engage a stop block 742P on the movable switch frame 750 as the switch rotates to the right hand turnout position. In the left hand turnout position, the underside of the stop structure 740P is engaged by a stop block 744P. Just prior to reaching either turnout position. the switch frame 750 is brought to a smooth stop in alignment for insertion of the primary supporting lock pins. The described stop structure acts as a backup support in the event the lock pins fail to be inserted, i.e., the weight of the switch itself and all vehicle induced loads force the movable switch frame a slight distance (approximately .06 inches) against the stop structure 740P. This self-alignment feature enhances the safety of the rotary switch. As shown in FIG. 10CB, stop end structure 740F is secured diagonally opposite the stop 740P. The stop 740F essentially operates like the point end rotational backup stop 740P. Stop block details are shown in FIGS. 8EJ and 8EK. 
     When the double turnout switch frame 750 is in the right turnout position shown in FIG. 8E or in the left turnout position (not shown). a vehicle moving over the switch always applies a portion of its weight only to the turnout beam 756 through the tires on the left side of the car (right turnout) or the tires on the right side of the car (left turnout). Accordingly, the force of the vehicle weight always (right or left turnout) tends to rotate the switch frame 750 about its axis of rotation toward the safety rotational stops 740P and 740F. 
     As an additional safety feature, vehicle wrong entry guidewheel stops are provided to keep a vehicle locked on the guideway if the vehicle enters a switch with the switch aligned for the turnout position opposite to the turnout on which the vehicle is located. A stop 778L (FIGS. 8EA and 8EE) provides protection in the left hand turnout position of the switch and a stop 778R provides protection in the right hand turnout position of the switch.